EP0307417A1

EP0307417A1 - Rotating piston machine.

Info

Publication number: EP0307417A1
Application number: EP88900037A
Authority: EP
Inventors: Laszlo Maday
Original assignee: Individual
Current assignee: Individual
Priority date: 1987-03-25
Filing date: 1987-12-10
Publication date: 1989-03-22
Anticipated expiration: 2007-12-10
Also published as: HU199592B; DE3777649D1; JPH0555692B2; WO1988007623A1; EP0307417B1; HUT48326A; JPH01502839A; AU8339387A

Abstract

Une machine à piston rotatif, en particulier un moteur suralimenté à piston rotatif, comprend par exemple un cylindre pourvu de canaux d'admission et de sortie et un piston rotatif agencé dans ce cylindre et relié en relation d'entraînement à l'arbre principal. L'espace intérieur (2) du cylindre (1) est de forme annulaire et permet au piston rotatif (3) de tourner avec l'arbre principal (5) coaxialement agencé par rapport au piston. En outre, au moins une soupape réglable d'arrêt (8; 19; 27) est agencée entre le canal d'admission (15) et le canal de sortie (16), cette soupape fermant de manière étanche la section transversale de l'espace intérieur (2) du cylindre (1) dans sa position fermée mais libérant, lorsqu'elle est mise dans sa position ouverte, l'espace intérieur (2) du cylindre (1) de façon à permettre le libre passage du piston rotatif (3).A rotary piston machine, in particular a supercharged rotary piston engine, for example comprises a cylinder provided with inlet and outlet channels and a rotary piston arranged in this cylinder and connected in drive relation to the main shaft. The interior space (2) of the cylinder (1) is annular in shape and allows the rotary piston (3) to rotate with the main shaft (5) coaxially arranged with respect to the piston. Further, at least one adjustable shut-off valve (8; 19; 27) is arranged between the inlet channel (15) and the outlet channel (16), this valve sealingly closing the cross section of the valve. interior space (2) of cylinder (1) in its closed position but freeing, when it is placed in its open position, interior space (2) of cylinder (1) so as to allow free passage of the rotary piston ( 3).

Description

ROTARY PISTON MACHINE, IN PARTICULAR CHARGED CYLINDER ENGINE

TECHNICAL AREA

The invention relates to a rotary piston machine, mainly a supercharged rotary piston engine, which can be used, for example, in motor vehicles or as a stable engine, or as a compressor or as a pump.

STATE OF THE ART

As is known, inventors have long attempted to create such a volume-displacing internal combustion engine with a rotary movement instead of the linear, alternating piston movement. In practice, a number of such rotary lobe machines or rotary lobe motors have become known, but only the "WANKEL engine" can be regarded as relatively widespread among them. (See, for example: Dr. ABRAHAM: "Handbuch der Straßenverkehr", Technische Buchverlag, Budapest, 1978, pages 745-746.)

In the WANKEL engine, the piston is actually an internally toothed planet gear, ie a wheel rim. The outer contour of this ring gear is not circular, but a triangular structure consisting of a circular arc, which has the same diameter in every direction. If the crank handle is turned, the ring gear, ie the rotary piston, describes cycloid tracks. The so "abge from the rotary lobe swept "surface thus has almost the shape of a peek. If this base surface is now surrounded by a jacket, this actually results in the cylinder of the engine.

The above rotary engine is of a much simpler design than the conventional reciprocating engine. Nevertheless, according to experience to date, a serious obstacle to its widespread distribution is that the top sealing of the Kolgens is problematic; furthermore, the connection between cylinder and piston, as well as the engine control is too complicated and too expensive with regard to the design, and therefore requires too much material and a higher generation technology.

PRESENTATION OF THE INVENTION

With the present invention, we aimed to overcome the above shortcomings, i.e. to create such a rotary piston machine, which is comparatively cheaper and structurally simpler, and therefore requires relatively little effort, on the other hand ensures widespread use in the various fields of application.

To solve the problem we started from such a rotary lobe machine, which has a cylinder provided with an inlet channel and an outlet channel, as well as a rotary piston installed in the interior of the cylinder, the rotary piston also being in drive connection with the main shaft of the engine. This invention was further developed so that the interior of the cylinder was made circular, in which the rotary piston was mounted coaxially with the cylinder surface, but rotating together with the main shaft is arranged. In addition, a damper valve is provided between the inlet channel and the outlet channel, which seals the cylinder chamber in the closed position, but controls the cylinder chamber in the open position in a controlled manner - for the unobstructed passage of the rotary piston.

The rotary lobe machine according to the invention can preferably be used as a supercharged rotary piston engine, in which the inlet channel is provided with a controlled inflow valve, as well as with a unit that feeds the combustion air or a combustible gas mixture with compressed air (e.g. with a compressor). Furthermore, a filling section, a working cycle section and an exhaust section are provided in the circular interior of the working cylinder. In the filling section, the cylinder is provided with such a unit, which can work as a fuel injection nozzle in diesel engines, but as a spark plug in gasoline engines.

The rotary piston is expediently designed as a radial extension on a traction sheave which can be rotated in conformity with the main shaft. Together they form the rotor of the machine.

According to a further feature of the invention, such an embodiment is also possible in which the cylinder in the work cycle section is also provided with a second damping valve, in front of which a regulating valve for the supercharging pressure is arranged, taking into account the direction of rotation of the rotary piston. As a result, the charge pressure of the engine can be regulated within wide limits from the purge side. Such a further embodiment of the rotary piston machine according to the invention is also possible, in which partly a rotary piston engine and partly a compressor can be operated in a single cylinder. For this purpose, a third damping valve is arranged between the first damping valve and the outflow channel, and the cylinder is provided with an air inflow valve and an air outflow valve between the first and third darm valves. In this section, the cylinder interior also forms a compressor in cooperation with the rotary piston.

It is also expedient if the insulating valve is designed as a radially displaceably mounted slide. The insulating valve, however, can also be designed as such a rotatable disc, which is arranged normal to the rotary plane of the rotary piston, in the transverse direction thereof. This rotatable disk is at least provided with such an opening which is able to let the rotary piston pass through; further connected to such a rotary drive, which is controlled depending on the rotation of the rotary piston.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will now be explained in more detail with reference to the accompanying drawings. These show two exemplary embodiments of a supercharged circular piston engine according to the invention as follows:

Fig. 1 - section of the first embodiment of the rotary piston engine according to the invention;

Fig. 2 - cross section of the solution of Figure 1 on a relatively smaller scale. Fig. 3 - second embodiment of the rotary piston machine according to the invention, shown in section;

Fig. 4 - Detail of the solution of Fig. 3 as a preferred embodiment in plan view, partly in section.

PREFERRED EMBODIMENTS

1, an annular inner space 2 is formed in a cylinder 1, in which a rotary piston 3 can be rotated in a sealed manner. The rotary piston 3 is in the illustrated case al3 radial attachment of square-prismatic cross section fastened to a drive disk 4, which is arranged so that it can be rotated with a coaxially embedded main shaft 5 of the motor. The main shaft 5 is mounted in a motor housing in a manner known per se and is connected to a drive of a vehicle via a shaft coupling (not shown).

The cylinder 1 is provided with an inlet valve 6 and an outlet valve 7, which are used to open or

Serve to close the inlet duct 15 or the outlet duct 1. According to the invention, an insulation valve 8 is additionally installed between the inlet duct 15 and the outlet duct 16, which seals off the interior 2 of the cylinder 1 in the closed position, but in the open position releases its entire cross-section so that the rotary piston 3 can pass freely over the entire circumference. In the present case, the insulation valve 8 is designed as a slide which can be rotated to seal in a longitudinal groove and which shifts a control mechanism (not shown) from the closed position shown in FIG. 1 to the open position. This can be, for example, a control device cooperating with a control surface of the main shaft 5.

In this case, the rotary piston engine is a supercharged engine (compressor engine) which, via the inlet valve 6, pressurizes the combustion chamber with combustion air in a diesel mode of operation; or filled with a combustible gas mixture in gasoline engine mode so that the final compression value is reached in the predetermined angular position of the rotary lobe 3. Said fuels are then burned by self-ignition of the diesel oil then injected at this point in time (in diesel mode of operation) or by spark ignition of the combustible gasoline-air noise (in OTTO engines). The energy released thereby rotates the rotary piston 3 - together with the main shaft 5 - in the desired direction of rotation of an arrow 9.

In the present case, the ring-like interior 2 of the cylinder 1 permits the full rotation of the rotary piston 3 by 360 °. With the reference symbol "A" in Fig. 1 is the

Basic position of the rotary lobe 3 at the start of charging, but designated "B" by the position of the rotary lobe 3 which it occupies at the time of the explosion. A section of the arc between "A" and "B" therefore represents the charging section 10 of the interior 2. Furthermore, the reference symbol "C" denotes the rotary piston position at the end of the work cycle. Between positions "C" and "B" there is an arcuate work cycle section 11. Finally, "D" denotes the position of the rotary piston 3 at the end of the exhaust cycle, ie there is an exhaust section 12 of the interior 2 between the positions "C" and "D", between the position "D" and "A" but the transition section 13 is.

In our tests, the radius "R" became the drive

"M" disc 4 with 100 mm, its height / but with 50 mm, further in the embodiment according to FIG. 1, the charging section

10 of the interior 2 with 90 °, the work cycle section

11 with 180 °, the exhaust section 12 with 60 °, but the transition section 13 with 30 °.

The cylinder 1 is provided in the supercharging section 10 with such a unit 14 which, in a manner known per se, is a fuel injection nozzle in the diesel mode of operation, but is an electric spark plug in the gasoline engine mode of operation.

In Fig. 2 it can be seen in cross section that the cylinder 1 and the engine block assembled with it in the present case is divided, furthermore the lower seal of the rotary piston 3 is provided in a manner known per se by sealing rings 17, which on the end faces of the Drive pulley 4 rest on both sides. If necessary, the cylinder 1 can be provided with cooling fins 18 on its outer jacket.

The supercharged rotary piston internal combustion engine according to FIG. 1 works as follows:

The inlet is in the "Ä" position of the rotary piston 3 valve 6 opened, however, the isolation valve 8 is found in the closed position. Now, feed air is pressed into the charging section 10 of the interior 2 via the inlet duct 15, for example for diesel operation, until the rotary piston 3 reaches the position "B". The outside compression of the air is selected so that when the position "B" of the rotary piston 3 is reached, the compressed air pressure reaches the planned compression end value and the temperature corresponding to it. The unit 14 (here: through the injection nozzle) then burns the gas oil injected into the space 2 by self-ignition. It should be noted that during operation in the charging section 10, the cylinder volume between the rear end face of the rotary piston 3 and the insulating valve 8 continues to increase. Nevertheless, the necessary operating pressure and the temperature for the firing must be secured by increasing the external compression. The operating mode according to the invention thus deviates from the thermodynamic diesel cycle to be regarded as classic. By regulating the charge, the specific power of the engine can be regulated within wide limits.

The expansion caused by the firing rotates the rotary piston 3 in the direction of the arrow 9. Meanwhile, the rotary piston 3 still performs the corresponding movements in the work cycle section 11. The exhaust section 12 is calculated in the present case from the position "C" of the rotary piston 3, while at open position of the exhaust valve 7, the gases located in front of the rotary pistons 3 in the space 2 are pushed out of the cylinder space via the exhaust passage 16. (We note that the exhaust valve 7 may be omitted if necessary.) When the rotary lobe 3 arrives in the "D" position, the exhaust stroke is ended, and then the transfer section 13 follows, after which the rotary lobe 3 has returned to its initial position "A", and the above cycle is repeated cyclically. If necessary, the inlet valve 6 can open somewhat before the position "A" of the rotary piston 3 is reached.

The internal combustion engine according to the invention works in a similar manner, even if it is used in the OTTO operating mode. A difference then only exists in that a gasoline-air mixture of a predetermined pressure is passed via an inlet duct 15 into the interior 2 of the cylinder 1 from a mixture formation device known per se (e.g. with a carburetor); further in this case the unit 14 is an electrical spark plug. The inlet valve 6 allows the mixture (compressed to the final combustion pressure with external compression and thus heated to the specified extent) to enter the interior 2 of the cylinder 1 through the inlet channel 16. This external compression, i.e. The cylinder chamber can be charged to the combustion pressure with any compressor known per se (e.g. a ROOTS compressor), so that further details are unnecessary here. The boost pressure depends on the selected operating method and the type of fuel.

A peculiarity of the rotary piston engine according to the invention is furthermore that the charging section 10 in the annular interior 2 of the cylinder 1 can be lengthened or shortened as desired. This means that the size can vary depending on the respective power requirement of the combustion chamber in an engine can be changed within wide limits. In other words, this means that the volume of the combustion chamber of an engine of an already selected size can be changed within wide limits, for which purpose only the beginning of the "B" position of the

Rotary piston 3 offset along the circumference, and of course the control of the valves must be changed accordingly.

3 shows a combined exemplary embodiment of the invention, the rotary piston engine being combined with a compressor.

With regard to the basic design of the internal combustion engine, this design corresponds to the design according to FIGS. 1 and 2. Here too, the inlet valve 6 can be found, as well as the outlet valve 7 and the insulation valve 8 installed between the two. The charging section 10 is chosen here at 90 °, the working cycle section 11 at 120 °, but the exhaust section 12 at 60 °.

In the work cycle section 11, the cylinder 1 is provided with a further damping valve 19 which can be configured and controlled identically with the damping valve 8. Before this, however (as seen in the direction of rotation of the rotary piston 3), the cylinder 1 is provided with a regulating valve 20, by means of which the charging pressure can advantageously be regulated by the cylinder space in front of the rotary piston 3. This can be particularly advantageous if the supercharging pressure can be regulated by the compressor only within narrow limits via the inlet valve 6. After the exhaust valve 7, the cylinder 1 is provided with a third insulating valve 21. (In the present case, this can be identical in terms of the structural configuration and the control / insulation valve 8.)

The cylinder space delimited by the insulating valves 21 and 8 works - in cooperation with the rotary piston 3 - as a compressor "K", for which the cylinder 1 is additionally equipped with an inlet valve 22 and an outlet valve 23. The compressor "K" may also be sufficient per se to generate the supercharging pressure of the rotary engine. The compressor "K" can also pass on the compressed air, for example, to a pressure accumulator (not shown) or for other purposes.

The charging pressure in the charging section 10 can be regulated via the regulating valve 20 with the compressed air introduced from the flushing side in front of the rotary piston 3. This compressed air can also effectively cool the rotary piston 3 and the cylinder 1. It also improves the composition of the exhaust gas located in the cylinder space, i.e. the quality of the volatile exhaust gases (exhaust gases).

The transfer section 13 mentioned in the first embodiment is covered here by the rotary piston 3, starting with the closing of the outlet valve 23 to the basic position "A".

In Fig. 4 we give an example of how the insulation valves 8, 19 and 21 can be advantageously carried out. As it was shown here on a somewhat reduced scale, For example, the insulation valve can be designed as a disk 25 which can be rotated about a shaft 24 and which is provided with at least one passage opening 26 for the passage of the rotary piston 3. The disk 25 engages in the cylinder 1 radially and on the plane of the ring-shaped inner space 2 in such a way that it can rotate in a groove 27 of the cylinder 1 in a sealing manner around the shaft 24 embedded outside the interior. The shaft 24 is connected to a rotary drive (not shown), preferably to a clock drive known per se, which, depending on the respective position of the rotary piston 3, either rotates the disk 25 into a position such that from there it passes through the passage opening 26 of the rotary piston 3 can pass freely, or conveys the disc 25 into such a position that its full disc part closes the interior 2 of the cylinder in a gas-tight manner. With this embodiment, a silent and relatively simple working and controlling the insulating valves 8, 19, 21 can be achieved. Of course, the control must be designed so that the insulation valves 8, 19 and 21 open and close according to the above-described mode of operation.

Although we have only given an example in the above for the internal combustion engine, the rotary piston machine according to the invention can optionally also be used advantageously as a pump or as a compressor. Furthermore, such a design is also possible in which the insulation valve or the insulation valves (e.g. counter to a compression spring) is opened by an end face of the rotary piston 3 designed as a control track.

One of the main advantages of the solution according to the Er invention is that the rotor can be well balanced, which means that the machine can run smoothly and without vibrations even in high speed ranges. Furthermore, it is also advantageous that the cylinder and the rotor are extremely simple in terms of their structural design and can therefore be built with relatively little effort. The crank drives (crankshaft, plenum rods, etc.) that have so far been absolutely necessary in conventional engines can be left out here. This further simplifies or improves the design and operational reliability of the rotary lobe machine. It must be recognized, however, that bringing up the filling pressure requires additional effort than can be found in the supercharged engines currently used. However, this is compensated for by the fact that the operating parameters, namely the quality of the mixture, the supercharging pressure and the temperature can be controlled more precisely. However, more perfect combustion, better specific performance and more environmentally friendly gas emissions can be achieved with internal combustion engines. Since the speed can be increased to any extent (even in a range above 10,000 n / min), the performance of the internal combustion engine according to the invention can be significantly increased compared to the known solutions. In addition to gas oil and petrol, the internal combustion engine can also be operated with any other combustible gas mixture. Due to the coaxial arrangement of the main shaft 5, the load on the main shaft bearing is considerably cheaper than in conventional motors. Accordingly, the internal combustion engine according to the invention is also superior to the known gasoline engine types in terms of operational safety and service life.

Claims

PATENT CLAIMS

1. Rotary piston machine, in particular supercharged rotary piston, which has a cylinder provided with an inlet channel and an outlet channel, in the interior of which a rotary piston is movably arranged, the rotary piston being in drive connection with a main shaft, characterized in that the interior ( 2) of the cylinder (1) in the form of a ring, in which the rotary piston (3) with the main shaft (5) coaxially mounted to the interior (2) is rotatably arranged, furthermore at least one controlled one between the inlet channel (15) and the outlet channel (16) Insulation valve (8) is installed, which in the closed position seals the interior (2) of the cylinder (1), but in the open position to allow the rotary piston (3) to open the cross-section of the interior (2) of the cylinder (1).

2. Rotary piston machine according to claim 1, characterized in that it is designed as a charged rotary piston internal combustion engine, in which the inlet channel (15) is provided with a controlled inlet valve (6), and with one, the combustion air or the combustible gas mixture with a compression end pressure feeding unit, preferably connected to a compressor, and that a charging section (10), a working cycle section (11) and an exhaust section (12) are provided in the annular interior (2) of the cylinder (l), wherein the charging section (10) is provided with a unit (14) which is designed as a fuel injection nozzle or an electrical spark plug.

3. Rotary piston machine according to claim 1 or 2, characterized in that the rotatable with the main shaft (5) rotatable piston (3) is designed as a radial approach to a on the main shaft (5) attached drive disc (4), these together the rotor Form the machine.

4. Rotary piston machine according to claim 2 or 3, characterized in that the cylinder (1) in its working stroke section (11) is also provided with a second controlled damping valve (19), in front of which

- With the arrow (9) indicating the direction of rotation of the rotary piston (3) - a regulating valve (20) is arranged.

5. Rotary piston machine according to one of claims 2-4, characterized in that a third controlled damping valve (21) is installed between the first damping valve (8) and the exhaust valve (7) of the exhaust duct (16), wherein between the first and the third Insulating valve (8 and 21) of the cylinder (l) with an inlet valve (22) and an outlet valve (23) and de interior (2) is designed as a working space of a compressor (K) interacting with the rotary piston (3).

6. Rotary piston machine according to one of claims 1-5, characterized in that the insulation valves (8, 19, 21) are designed as radially displaceable controlled slides.

7. Rotary piston machine according to one of claims 1-5, characterized in that the insulating valve (8; 19; 21) on one, on the rotational plane of the rotation piston (3) normal plane, and is arranged on this in the transverse direction, rotatable disc (25), furthermore the disc (25) is connected to a displacement mechanism controlled depending on the rotational position of the rotary piston (3).

LIST OF REFERENCES

1 - cylinder

2 - circular interior

3 - Rotary piston 4 - Drive disc 5 - Main shaft 6 - Inlet valve 7 - Outlet valve 8 - Insulation valve

9 - arrow

10 - charging section

11 - Work cycle section

12 - Exhaust section

13 - transition section

14 - unit

15 - inlet duct

16 - exhaust duct

17 - sealing rings

18 - cooling fins

19 - Isolation valve 2C - regulating valve 21 - isolation valve

C d. - inlet valve

23 - outlet valve

24 - wave

25 - disc

26 - passage opening

27 - groove R - radius of the drive pulley M - height K - compressor

A - position of the rotary piston B - position of the rotary piston C - position of the rotary piston

D - position of the rotary lobe